Transmission control



April 7, 1953 c; A. NERACHER ETAL 2,633,948

TRANSMISSION coNTRoL Filed April 11, 1946 e sheets-sheet 1 La gl AP 7, 1953 c. A. NERACHER ETAL 2,633,948

TRANSMISSION CONTROL 6 Sheets-Sheet 5 Filed April 11, 1946 April 7, 1953 Filed April ll, 1946 C. A. NERACHER ETAL TRANSMISSION CONTROL 6 Sheets-Sheet 4 April 7, 1953 C. A. NERACHER ET AL TRANSMISSION CONTROL Filed April 11, 1946 6 Sheets-Sheet 5 INVENTORS.

April 7, 1953 C. A. NERACHER ETAL 2,633,948

rI-`RANSMISSION CONTROL Filed April 11, 1946 6 Sheets-Sheet 6 `mission control system Patented Apr. 7, 1953 TRANSMISSION CONTROL Carl A. Ncracher, Detroit, and Maurice C. Robin son, Royal Oak, Mich., assignors to Chrysler Corporation, Highland Bark, Mich., a corporation of Delaware Application Apri1`11, 1946,seria1No. 661,298

6 Claims.

Our invention relates to motor vehicles and refers more particularly to power transmission and control mechanism therefor.

It is an object of our invention to provide a transmission system affording improved characteristics of change speed control with 'a comparatively simple mechanism capable of long life.

A further object is to provide a control system that may be superimposed on a conventional manually operated transmission and clutch without necessitating expensive construction changes in either the transmission or clutch.

Another object is to provide an improved transincorporating both manual and automatic change speed control.

We have provideda power operating system for controlling the operation of the change speed means that is relatively simple in construction so that it may be economically manufactured. We have chosen the differential air pressure derived from utilizing the engine intake suction or vacuumf as Ait-is commonly called, for a power source. y Y

A further object of our invention is to utilize our transmission control in conjunction with a fluid coupling andto provide means to effect a clutch disengagement, a step-down in the transmission speed ratio drive from a relatively fast to -a slower speed ratio drive and a reengagement of said clutch during a retardation of thevehicle speed below a predetermined speed. The predetermined vehicle speed may be selected to be the vehicle speed at which sudden reengagement of the clutch can occur without producing a perceptible change in vehicle speed. This predetermined vehicle speed is established as the vehicle :speed at which the driven clutch elementsare "in synchronous speed relationship with the driving clutchy elementsimmedlately after the Stepdown in transmission speed ratio driveand when 'the driven clutch elements are rotating at a rela- Atively fast speed compared to thevehicle speed due to the operative connection between trans- :mission driving .elements and the clutch driven elements. .The speed of rotation ofthe driving 'clutch elements is controlled by the engine Speed whenitis idling under coast conditions with the clutch disengaged and no load on the engine. Under these conditions the above reengagement ofthe clutch will occur when the driving and driven elements-are rotating 'at substantially the same speed and substantially no sudden change in vehicle speed or lurch will be' produced thereby... The presence of a fluid coupling permits the vehicle speed retardation to continue until 'a' substantially zero -velocity .is obtained `without engine stall. The engine is able to idle with,l the vehicle stationary and the clutch eneased because f, the Slipping drive .connection made at the fluid coupling. Thereafter, upon acceleration a favorable torque multiplication is provided by the slower speed ratio drive and the increase in efficiency of the fluid coupling during acceleration.

According to our present embodiment of our invention we havev utilized a transmission employing countershaft gearing and providing three forward speeds and reverse. The driver may be manually selecting automatic control and placing the shift lever in the position normally referred Ito as second speed position be provided with automatic change speed control between second and third forward speeds which will be adequate under normal driving conditions. .First speed may be manually selected andused as an emergency low. ,1 An additional object of the invention is to com- .bine a movable transmission element adapted to change a transmission speed ratio drive with a novel automatic .means forcmovinggthis element and with a manual means for moving the element. The` automatic means has a cushioning means included in its operativeconnection with the element and the manual means is able to operate the element .independently of the cushioning means. lThe automatic means, particularly where it is `actuated by a vacuum cylinder, moves morerapidly than the transmission change in speed ratio drive can be effected.` ,It is there- .fore necessary to incorporate ya delaying means into the automatic means to 4delay the movement of the transmission components so that they may operate quietly and to their best advantage and so that the clutch disengagementcan be assured prior to the effecting of the change in transmission-speed ratio drive. Manualcontrol `does not require this delayand therefore means are provided herein for manually operating the-transmission element lindependently ofthe delaying means.

An important feature of our invention is that if theautomatic controls are completely inactivated manu-alcontrol of the transmission is still possible.

To` actuate the control system we have utilized a single vacuum cylinder providedwith valving and adoubleactingA piston. Sufficient motion of this piston in one direction `will effect a clutch disengagement, a-speed ratio change and a clutch reengagement. f

AAdditional features of o ur invention are found in the provision of many features of improved construction and functional operation which will be more apparent from the following illustrative embodiments of the principles of our invention, reference-beinglhad to the accompanying drawings in which: Y 1xFig. 1 is a side elevational view of the power plant and transmission for a motor vehicle;V

Fig. 2 is a plan view of the steering wheel and driver operable vshift lever as viewed by the vehicle driver;

Fig. 3 is a longitudinal sectional elevational view through the main clutching mechanism;

Fig. 4 is a similar view through the transmission;

Fig. 5 is a diagrammatic view of the control mechanism;

Fig. 6 is a sectional elevational view of a portion of the mechanism carried by the transmission housing; l

Fig. 7 is a section on the line 1 7 of Fig. 6;

Fig. 8 is a section on the line 8 8 of Fig 6;

Fig. 9 is a side elevational view similar to Fig. l but is a somewhat larger view containing more detail;

Fig, l is a plan view of the Fig. 9 mechanism;

Fig. l1 is a sectional elevational view of the mechanism for selecting manual or automatic control;

Figure l2 is an enlarged view illustrating the switching means on the shift control mechanism;

Fig. 13 is a section on the line yI 3-l 3 of Fig. .12;

Fig. 14 is an `enlarged view of the lost motion connection between the actuating piston and the transmission speed ratio control element; and

Fig. l is a perspective view of one link in the over center toggle of the clutch release mechanism.

In the drawings A represents the internal combustion engine which drives through fluid coupling B and conventional type of friction main clutch C to the speed ratio transmission D from which the drive passes from the output shaft V20 to drive the vehicle rear wheels in the usual manner.

The engine crankshaft 2l carries the vaned fluid coupling impeller 22 which in the wellknown manner drives the vaned runner 23 whence the drive passes through hub 24 to clutch driving member 25. This member then transmits the drive, when clutch C is engaged as in Fig. 3, through driven member 2S to the transmission driving shaft 27 carrying the main drive pinion 28. A clutch pedal 29 controls clutch C such that when the driver depresses this pedal, yoke 11 and collar 30 are thrust forward to cause levers 3l to release the clutch driving pressure plate 32 against springs 33 thereby releasing the drive between runner 23 and shaft 21. The primary function of the main clutch C is to enable shifts to be made manually or automatically in transmission D.

Referring to the transmission,y the main drive pinion 28 is in constant mesh with the gear 40 of the countershaft gear cluster mounted for rotation on the countershaft 4 I. This gear cluster, according to well-known practice, comprises a low speed gear 42, a second speed gear 43, and -a reverse gear 44, which is in constant mesh with the reverse idler gear 45. The transmission output shaft 2G extends rearwardly to drive the ground wheels of the vehicle.

The driven shaft 46 integrally connected to output shaft 20 has mounted thereon the low speed and reverse gear 41 splined to the driven shaft for selective meshing with the countershaftlow speed gear 42 or the reverse idler gear 45 for respectively transmitting a low speed drive to the driven shaft l5 or the drive thereto in a reversed direction. Freely rotatable on shaft 46 is the second speed gear 48 in constant mesh with the countershaft gear 43 for transmitting a second speed ratio drive. The gear 28 drivingly carries a set of circumferentially spaced external clutch teeth 4S. VIn a similar manner the gear 48 drivingly carries a set of clutch teeth 59.

splined on the shaft 4B adjacent the forward extremity thereof is an axially shiftable collar or sleeve 5|. vBlocker teeth rings 52 and 53 are carried by sleeve 5l and adapted for slight rotation relative to sleeve 5| whereby synchronizing of gear speeds prior to clutching of shaft through collar 5I with either gears 28 or 48 is effected in a manner well-known in the art.

The transmission is illustrated in its neutral position. To establish the direct or high speed driving connection between shafts 2 and 2B, the' collar 5l is shifted axially to the left as viewed in Fig. 4 `by the control means hereinafter described. to `engage the teeth 49 drivingly connected to the gear 28 carried by the driving shaft 27, and when so connected, the collar is drivingly carried by the shaft 46. The second speed driving connection is established lby similarly moving the' collar 5l to the right as viewed in Fig. 4 to engage teeth 59 carried by gear 48. The first or low speed is obtained by moving gear 4'! which is splined to driven shaft 20 forwardly in Fig. 4 into engagement with countershaft low speed gear 42. The drive then occurs from shaft 2 through main drive pinion 28, countershaft gear 43, countershaft low speed gear 42, gear di, and driven shaft 29. Reverse drive is obtained by engaging `gear 4l with reverse idler gear 45. The transmission mechanism thus described is an embodiment conventionally employed in motor vehicles.

When manual operation has been selected by the vehicle driver in a manner to be described herein, the drives are selectively controlled by operating lever and clutch pedal 29. Clutch pedal 29 is mounted on lever 59 which is rotatably mounted on shaft 63 shown in Fig. 10 as attached to the usual master cylinder El Aof the vehicles hydraulic braking system. It is to be understood that shaft 60 could be aflxed to the vehicle frame 52 or any other stationary member. Lever 59 is provided with extension 63 extending beyond shaft E5. Bolt 64 fastens forwardly extending rod 65 to extension 63. Rod 65 is rotatably mounted at 56 on arm 61 rotatably mounted on shaft 59. Shaft 58 is rotatably mounted by a ball and socket joint on arm 69 fastened to flexible plate 70 which is fastened to clutch housing 53 at 5l. Arm 59 and plate i3 support one end of shaft 68. The outward end of rod 58 is also provided with a ball and socket connection at i2 with member 13 fastened to frame 62.

The ball and socket joints and flexible nature of plate 'l0 prevent the transmission of engine vibration to clutch lever 59. A downwardly projecting leg l5 rotatably carried by shaft 58 has rearwardly extending rod 'I6 rotatably fastened thereto. Rod I6 is fastened to clutch fork 77. Overcenter Spring 18 has one end fastened to the frame (Fig. l) and the other end, through rod a, fastened to extension 19 of arm 61.

Depression of clutch lever 59 rotates extensions 63 counterclockwise about shaft 6U and retracts rod E5. The rearward movement of rod 55 rotates arm 61 in a counterclockwise direction and through lugs 8| and 82 moves leg 'l5 and rod 75 to the right in Fig. 5. This pivots bifurcated clutch fork 'I7 about fulcrum 80 (see Fig. 5) and disengages clutch C. Overcenter spring 'I8 assists the driver in the last portion of movement required to disengage clutch C. Spring re- 1 `finger |04 moved fork |05 or i03.

turns the'mechafnism toits Fig. 9` position when the driver releases'fpeda129. y l

Manual operation of gearshift lever 55 may be utilized tocontrol the transmission. Lifting lever 55 in a plane containing thecontrol rod 90 will through Bowden wire 9| control transmission selectorv lever` 92. .Rotationnof lever 55 from position E to position E' or Efxin Fig1f2 .will through the link and lever system 34,` 35, 38 to the transmission control shaft 31 Ithereby operate v-the transmission speed ratio control element which has been selected by longitudinal movement of rod 90.

" Transmission D is providedwithV control means comprising selector cam keyed to shaft |0| which is keyed to selector lever 92. Lifting lever 55 pulls Bowden wire 9|"and rotates lever`- 92,

shaft |0| andcam |00. The outward end of cam |00 is lifted by this movement. 'Control shaft 31.(Fig. 6) is rotatably mounted in the `transmission housing. @Cylindrical lever 02 sur'- rounds shaft 31`-`and pin |03 mounted normalto the axis of the shaft fastens the lever. to the shaft. Relative axial rotation is prevented by pin |03 but slightyrotation of'lever |02':on' pin |03..is

possible. Cylindrical lever` |02 'is provided with nger |04 adapted `to penetrate the openings provided in' forks |05and'lll6` on shift rails |01 and |08. Spring |09 urges nger |04' to its downward position. 'Fork |05 engages cellar 91 on f:

low'speed and"reversegear 41'. VFork ite engages collar 51: for-selecting second ordirect'transmission drive?r Gearshift fork guide rail |44 supports theA weight `offorksv |05 and |00. As illustlated'inl'iig.` 6 finger |04 is'normally in engagement with'th'e rforkA |06 onthes'econd speed and fold vacuum or low pressure in' cylinder or compartment of housing 09 is the source of powerfor actuating the 'clutch release fork 11 and transmission fork |05. Solenoid controls and switches are provided to control the time and direction of movement of piston H0. ||2 is provided so that the vehicle driver may `select manual or automatic transmission control.

In Fig. 5 the usual grounded storage battery ||3 supplies electric energy through ammeter H4 to manual dash switch H5 thence to switch H9 provided on the lower end of the shift control rod 34. Switch H6 is adapted .to be closed through terminals 94 and 95 (Fig. 13) when the 'shift lever 55 is in its second speed or lower E position. Int-,his position the terminals 94 and 95 are in contact. In the direct drive or lower El position of the shift lever the terminals are in the same plane normal t0 the control shaft but on diiferent radii. In the reverse drive or upper E" position of the control lever the control f rod and terminal 94 are lifted and terminal 04 is above terminal 95. Lug H1 will prevent the contact of terminals 94 and. 95 by holding terminal 94 in its upper position. Whenv the control lever is placed-in lthe low speed or `upper E A selector titl position', the terminal 94 is lifted and rotated relative to terminal 95. L

Switch ||6 is connectedY in parallel .to, two secondary circuits at ||8. `The. first of these secondary circuits' leads to solenoid ||9 controlling valve |20. Solenoid H9V is grounded at V|2|. Valve |20 is interposed between line |22 connectedto the engine .manifold andline |23 directedftocylinder.|||;` When solenoid ||9 is energized line |22isI connected to line |23 and when solenoid ||9 is deenergized the valve |20 is spring returned to closed position, venting line |23through screen 98. The second secondary circuit leads from connection I8 through switch |24 adapted tobeY closed whenthe'usual accelerator pedal |25 is released by the operator and springfreturnedto its normal upward position. A centrifugal vehicle Vspeed responsive governor |26 driven from some suitable source such as gear |21 in Fig. 4 is adapted to connect terminal |28"withA terminal '129 above a Vvpredetermined vehiclespeed; Spring |30 disconnects `terminal |28 from terminal |29 and engages 'terminal |28 with terminal |3| below this' predetermined vehicle speed. Terminals |29 and"|3|lv are elec# tricallyeonnected togroundedsolenoids' |32 and |33 'respectively'by leads |34 and'|35. Sole'rioids |32`fand |33 control valvesi"-|36 and |31 which selectively' open and close portsf |38 and |39 connectirig line |23"with opposite Vends .of cylinder Hl." Valves '|38 and |31 are spring returned to closed position as by spring `93 when their solenoids 'are deenergivzed.' The ends of 'cylinder are vented through screens 81e and 82a when the valves are closed.

Selector |"|2 is connected by' line |40 with line |23. VReferring to Figs. 5, ll, and 6 the construction of the selector is illustrated. Three parallel plates |4I, |421 and |43 comprise Ythev power transmitting mediums. Middle plate |42 is keyed to the transmission control shaft 3.1. Plate |4| is operatively fastened to manually controlled rod 33. Plate |43 isoper'atively fastened to rod |45 which is operatively connected in a manner to be described herein to piston |'|.0. Plates I4! and |43`are both rotatably mounted ontransmission# control shaft 31. Meansfare provided to'selectively connect plates I 4| or` |43 to "plate |42. Each plate isr provided with a transverse circular opening |46 ,1 |41, or |48. The openings arefoi uniform diameterl Aspherical ball |49 is positioned inv opening |41I of plate |42.A The thickness of` plate |42 approximates theradius of bau |49. Hence, when bali |49 is aiigried'with one surface of kplate` |42nits widest portion is aligned with the-"opposite surface of plate |42 and approximately one-half its volume has peneti'ated the opening in plate |41 or |43. There'- forefthe position of ball |49 determines which rotatable"platev is lockedto plate |42.

Spring |50 and plunger llprovided in plate '|41 urge ball |49 into the opening |48 in plate |43. Plunger |32'and 'spring |53 urgeball |49 vtoward plat'e |4|. VSpring |543 is stronger than spring |50.A Diaphragm |55 fastened to plate |43 deinesa chamber 2|54connected to a source of manifold suction vorvacuumby line |40 so asto overcome'spring |53"and retract plunger |32 when air` is 4withdrawn from chamber |54. A b leedhole 83 is provided inthe wall of chamber |54.r Therefore, when al partial vacuum exists in' chamber |54 spring |"53 is overcome 'and spring |50 forcesball |4'9intov opening'lll in plate 43 thereby operatively'connecting :plates |42 and *143: to leffect*'control of, transmission shaft 31 `by piston ||0. When Yatmospheric pressure exists in chamber |54 spring |53 overcomes spring |50 and forces the ball |49 into opening |46 in plate 4|. This operatively connects plates |4| and |42 to effect control of transmission shaft 31 by manually controlled rod 36. Slot |58 in plate |4| and spring |56 and ball |51 in the transmission housing cooperate to restrain movement of plate |4| out of its neutral position. Plate |42 is always operatively connected to one of plates |4| or |43 and the opening in the third plate must be aligned with ball |49 before a transfer in operative plate connections can be eifected.

Referring to Fig. 5 piston rod |60 is illustrated fastened to piston ||0. Means to disengage clutch C are connected to the end of piston rod |60. An overcenter toggle comprising legs |6| and |62 is rotatably fastened to piston rod |60. Leg |6| is rotatably fastened at |63 to a fixed surface such as the frame. connected at |66 to one leg |64 of a bellcrank. The other leg of the bellcrank has fastened thereto a rod 16 connected to clutch fork 11. Leg 62 of the toggle is adapted to transmit force in one direction only. Leg |62 is composed of two relatively slidable portions |622 and |6211. Portion |62b has a track |10 and abutment |1| formed thereon. Therefore, portion |62a when pushed against abutment |1| will transmit force but unobstructed relative motion in the opposite direction is permitted. This connection is used so that when clutch pedal 29 is depressed, rod 65 retracted and the bellcrank rotated counterclockwise to manually disengage clutch C the rod 60 and piston H0 will not be disturbed. The bellcrank is mounted on shaft 68. One complete stroke of piston ||0 will disengage and reengage clutch C. For example, as piston ||0 moves to the left in Fig. 5 piston rod |60 straightens toggle |6| and |62 increasing the distance between points |63 and |66. The counterclockwise rotation of the bellcrank moves rod 16 and the lower portion of clutch form 11 to the right in Fig. 5 thereby disengaging clutch C. Further movement of piston rod |60 brings the toggle legs |6| and |62 over center and permits springs 33 to reengage clutch C.

A lost motion connection (Fig. 14) |15 is provided between piston rod |60 and transmission shift control rod |45. Piston rod |60 is provided with abutments |16 and |11. A spring |80 surrounds rod |60 and engages slidable members |8| and |82. Housing |83 is provided with abutments |84 and |85 and lug |86. Transmission shift control rod |45 is fastened to lug |86. rod |60 is moved to the left in Fig. 5 rod abutment |16 carries member 8| and spring |80 is compressed between member |8| carried by the rod and member |82 engaging housing abutment |85. When spring |80 has been compressed beyond a predetermined point it overcomes the Leg |62 is rotatably r force required to actuate the transmission mechanism and moves housing |83, lug |86, and rod |45 to the left until member |82 engages abutment |11 of rod |60. A similar motion occurs when rod |60 moves to the right in Fig. 14. Abutment |11 on rod |60 picks up member |82 and compresses spring |80. When the spring pressure becomes suiciently great the spring moves member |8| and housing |83 to the right until member |8| engages rod abutment |16. Rod abutments |18 and |19 are provided to initiate the housing motion in the event of spring failure.

In operation our automatic control is initiated by closing dash switch I5 and placing shift lever 55 -in its second speed or lower E. position there'- by closing switch ||6. The transmission is now in its second speed drive because it was manually placed therein by the above movement of shift lever 55. Accelerator pedal |25 is depressed as the vehicle accelerates in second speed drive. When the predetermined vehicle speed has been reached governor |25 overcomes spring |30 contacting terminals |28 and |29. The driver then releases accelerator pedal |25 closing switch |24 thereby initiating an upshift. Under these conditions electrical energy from grounded battery ||3 passes through ammeter ||4, dash switch 5, switch H6, point H8 and solenoid ||9 to ground |2|. This energizes solenoid I |9 opening valve |20 and connecting line 23 to the manifold suction or vacuum. Manifold suction from line 23 withdraws air from chamber |54 causing diaphragm |55 to overcome spring |53 and permitting spring |50 to seat ball |49 in the openings in plates |42 and |43 thereby operatively connecting rod |45 and transmission control shaft 31. Finger |04 is in the opening provided in shift rail |06 which is connected to transmission sleeve 5| controlling second speed and direct drive transmission gearing. Electrical energy under the above conditions also passes from point ||8 through yaccelerator switch |24, terminals |28 and |29, lead |34, and through solenoid 32 to ground. The energizing of solenoid |32 opens valve |36 connecting port |38 with line |23. Valve |31 is vented at 82. Air is withdrawn from cylinder and piston I0 is moved from the left end (in Fig. 5) of cylinder to the right towards the piston position illustrated in Fig. 5. The initial portion of the piston movement straightens toggle |62 rotating the bell crank counterclockwise and disengaging clutch C. At this time further movement of piston ||0 causes spring |80 in lost motion connection |15 to move housing |83 to the right thereby moving lug |86 and rod |45 to the right rotating plates |42 and |43 of selector ||2 and rotating transmission control shaft 31. This rotation of control shaft 31 moves finger |04 to the left in Fig. 5 thereby shifting fork |06 and sleeve 5| to the left in Fig. 4 causing a transmission upshift to direct drive. Further motion of piston ||0 carries toggle |62 over center and permits springs 33 to reengage clutch C. The driver then depresses accelerator pedal |25 incident to normal driving and increased vehicle speed.

If under normal driving conditions the driver next wishes to bring the vehicle to a stop the accelerator pedal |25 is released to partially close the usual throttle and reduce engine speed. Switch |24 is closed by this action. When vehiole speed is reduced below a predetermined point governor |26 retracts permitting spring |30 to contact terminals |28 and |34 thereby energizing solenoid |33 through lead |35 and deenergizing solenoid |32. The energizing of solenoid |33 opens valve |31 connecting port |39 with line |23. Manifold suction then withdraws air from the left side of cylinder in Fig. 5 moving piston i0 to the left. The movement of piston l l0 straightens toggle |62 thereby disengaging clutch C. Further movement of piston rod |66 causes loaded spring |80 to react thereby moving housing |83, lug |86, and rod |45 to the left in Fig. 5. This rotates plates |42 and |43 of selector ||2 thereby rotating transmission control shaft 31 and linger |04 shifting fork |06 and collar 5| and preparing the transmission for a second speed drive through shaft 21, pinion 28, countershaft gears and43, gear 48 anddriven shaft 20 when further movement of piston pushes toggle |62 .overcenter permitting clutch C to reengage.

' It is considered an important feature of our invention that the above clutch reengagements have occured suddenly and particularly in the preceding paragraph of the above description before the vehicle has completely stopped.. The governor |25 initiates the lstep-down in the transmissionY speed ratio drive described above at a predetermined speed. This predetermined speed is established as the speed at which the sudden reengagement of clutch C `can occur withoutcausing any substantial sudden change in vehiclel speed or .lurchff When piston i has moved suiiiciently to disengage clutch C and initiate the movement of collar preparing the transmission for vaesecond speed drive it is desirable that at this time the llltch driving member 25 and driven member 12 be rotating at substantially the same speed so that when they are lreengaged a fflurchwill `not ,be produced. The clutch drivingmember 25 is at this time rotating at a speed determined by the engine speed under substantially closed throttle conditions. The speed' of rotation of the driven clutch member 26 is determined by the vehicle speed and the transmission speed ratio drive effected by the above movement of collar 5|;

Therefore, the governor |26 is setto be responsive tothe vehicle speed which will effectA the desired speed of rotation of theclutch driven member. 2li.. In this :manner reengagement of clutch C controlled by governor |25 at the proper vehicle speed will be synchronized so that its effeet upon vehicle speed will be negligible and no lurch will `be produced. The `continued retardation of vehicle speed under these substantially closed throttle conditions will .occur until the vehicle has come to a substantially stationary position. It is possible for the vehicle to bestationary with the engine idling and the clutch engaged because of the slipping drive connection `in fluid coupling B. The vehicle may remain stationary until the driver desires to resume motion. Depressionof accelerator pedal |25 will accelerate the vehicle in the speed ratio drive which waseffected by the above movement of piston lit. When suitable vehicle .speed has .beenvobtained a step-up in speed ratio drivemay` be initiated -as explained above.

If the driver `desires to change the transmission `control from automatic to manual the shift lever 55 is moved to the position corresponding to the transmission drive then in operation. This aligns the openings in plates |4l, |42, and |43.

Y The movement of shift lever 55 opens switch llt deenergizing solenoid IIS` `and closing valve |28. Dash switch H5 should also be'opene'd so that automatic control will not-be-initiated the next time lever 55 is moved to its second speed position. Spring |53 causes-balllgto penetrate the opening in Yplate |4| thereby operatively connecting rod 3B and control rod t`|.V Manual control of transmission Dbyshiftlever isthen possible. Manual controlof clutch C is yalways possible due to the slidingconnection in toggle leglZ. lif The lost motion connection |75 is so` positioned that its cushioning effectisfpresent in the linkage connecting the piston llllwiththe transmission control shaft 31. It is important that themanual linkage connecting shift controllever 55 with the transmission shift rails is operative independently of the resilient connection |15. When the selecvtor H2 connects plates |42 and |4I by means of 10 ball |49 they are disconnected from plate |43 and operate independently thereof so that the driver may make manual shifts independently of the lost motion connection.

We claim:

1. In a drive for a motor vehicle having an engine, the combination of a variable speed ratio transmission having driving and driven elements therein and a control element the directionV of movement of which selects the speed ratio between driving and driven transmission elements, a housing having a cylinder therein, a piston adapted to reciprocate in said cylinder, means for creating pressure differentials in said cylinder between the opposite sides of said piston to thereby selectively move said piston in either of two opposite directions, `a resilient connection'between said piston and said control element operable to transmit motion to said control element to move the latter in either. of two directions depending on the direction of movement. of,` 'said piston, a clutch adapted to drivingly connect and disconnect said engine from said transmission and having a control member, means operatively connecting said piston and said clutch control member whereby movement of said piston in either direction disengages and reengages said clutch before said resilient connection moves said transmission control element in response to movement of said piston.

2. In adrive for a motorvehicle having an enginethe combination of avariable speed ratio transmission, a normally engaged clutch adapted to drivingly connect and disconnect said engine with said transmission, a housing having a cylinder therein, a piston slidably mounted in said cylinder, means for effecting movement of the piston in either of `two directions'by inducing a pressure differential between opposite sides thereof, a piston rod, linkage containing an overcenter toggle operatively connected to said piston rod and said clutch whereby movement of said piston rod in either direction disengages and reengages said clutch, a housing slidably mounted on said piston rod, linkage connecting said housing with said transmission, abutments on said piston rod and said housing, a spring engaging said abutments whereby movement of said piston rod induces stress'in-said spring' which moves said housing when the stress exceeds a predetermined amount and whereby said transmission linkage is'actuated while saidrclutch is disengaged.

3. kIn a drive for. motor vehicle having an internal combustion'engine provided with an intake manifold, a throttle and an accelerator pedal, a variable speed ratio transmission provided witha manuallyoperable shift control rod having a first, a second, and a third forward speed position, a reverse position, and a neutral position, aclutch adapted to drivingly connect and disconnect Vsaid engine from said transmission, a housing having a cylinder therein, a piston `slidably mounted inl said cylider, means for effecting movement ofthe piston in either of two directions by inducing a pressure differential between opposite sides thereof, linkage connecting said lpiston Withsaid clutch`whereby movement of said piston in either ,direction disengages and reengages saidiclutch, linkage connecting said piston with said transmission adapted to select one .speed ratio drivein said .transmission'when said piston m'ovesin one direction and adapted to selectanotherspeed ratio drive in said transmission when said piston moves in the opposite direction, means to actuate said transmission linkage during the interval when said clutch is disengaged, an electrical circuit comprising a grounded source of electric energy, a rst switch operatively connected to said shift control rocl and adapted to be closed when said rod is in its second forward speed position and open when said rod is in any of its other positions, an electrical connection between said rst switch and said source, a rst airtight Iconnection between said cylinder and said manifold, a normally closed grounded solenoid valve in said connection, an electrical connection between said rst switch and said solenoid valve, a second switch operatively connected to said accelerator pedal and adapted to be closed when said accelerator pedal approaches a closed throttle position, an electrical connection between said first switch and said second switch, a twoway switch having one inlet and two outlet terminals, a vehicle speed responsive governor adapted to electrically connect said inlet terminal and one of said outlet terminals below a predetermined vehicle speed, and electrically connect said inlet terminal and the other of said. outlet terminals above said predetermined vehicle speed, an electrical connection between said second switch and said inlet terminal of said two-way switch, a second normally closed grounded solenoid valve at one end of said cylinder, a third normally closed grounded solenoid valve at the other end of said cylinder, an air tight connection between each of said second and third solenoid valves and said first connection, an electrical connection between said second solenoid valve and one of said outlet terminals and an electrical connection between the third solenoid valve and the other of said outlet terminals whereby movement of said piston by manifold suction is dependent upon the concurrent closing of said first switch, said second switch, and said two-way switch and the direction of motion of said piston is dependent upon the position of said two-way switch, said position being determined by vehicle speed.

4. In a control for a motor vehicle transmission and clutch having an engaged and disengaged position, a housing having a chamber therein, a member movably mounted in said chamber, means for creating pressure differentials in said chamber between the opposite sides of said member to thereby selectively move said member in z' either of two opposite directions, a release fork on said clutch, springs urging said clutch to engaged position, a rotatably mounted bellcrank having a rst and a second arm, linkage connecting the first arm of said bellcrank to said release fork, an overcenter toggle having two legs fastened for relative rotation and having one end of one leg thereof rotatably mounted on said second arm of said bellcrank and the other end of the second leg thereof rotatably mounted on a stationary pivot, said member being mechanically connected to said legs, whereby movement of said member in either direction will extend said toggle, rotate said bellcrank and disengage said clutch as said toggle approaches a position where said legs are parallel and whereby further movement of said member throws said toggle overcenter permitting said clutch springs to reengage said clutch.

5. In a motor vehicle having a clutch and a transmission, an element associated with said transmission and adapted to change the transmission speed ratio drive when moved, a control mechanism for said element and clutch comprising a double acting motor having a compartment and piston slidably mounted therein, said control mechanism including means for creating pressure differentials in said compartment to selectively move said piston in either of two directions, means to cause motion of said piston in either direction to disengage said clutch, move said element and reengage said clutch, said control mechanism including yielding means governing the movement of said element by said piston, and manual means to move said element independently of said yielding means, and manual means to disengage said clutch.

6. In a drive for a motor vehicle the combination of an engine, an accelerator pedal for controlling tne speed of said engine, a variable speed ratio transmission having a control element, a clutch adapted to drivingly connect and disconnect said engine from said transmission, said clutch having driving and driven elements therein, means to disengage said clutch, change the transmission speed ratio and reengage said clutch while the vehicle is in motion, said means comprising a housing having a compartment therein, a member mounted for movement in said compartment, means for creating pressure differentials in said compartment between the opposite sides of said member to thereby selectively move said member in either of two opposite directions, a resilient connection between said member and said transmission control element operable to transmit motion to said transmission control element to move the latter in either of two directions depending on the direction of movement of said member, means operatively connecting said member and said clutch and operable to disengage and reengage said clutch in response to movement of said member in either of said directions, said resilient connection accommodating disengagement of said clutch before said resilient connection moves said transmission control element in response to movement of said member and vehicle speed responsive means to initiate movement of said member in response to manipulation of said accelerator pedal to a predetermined position during operation of said vehicle under predetermined vehicle speed conditions.

CARL A. NERACHER. MAURICE C`. ROBINSON.

REFERENCES CITED The following references are of record in the le of this patent:

UNITED STATES PATENTS Number Name Date 995,637 Beskow Dec. l, 1908 2,098,691 Neff Nov. 9, 1937 2,129,259 Boughton Sept. 6, 1938 2,156,589 Hopkins May 2, 1939 2,177,662 miesrath et al. Oct. 31, 1939 2,241,071 Price May 6, 1941 2,257,674 Dunn Sept. 30, 1941 2,282,053 Hey May 5, 1942 2,319,515 Priebe May 18, 1943 2,322,479 Schjolin June 22, 1943 2,326,943 Hill Aug. 17, 1943 2,328,921 Neff Sept. 7, 1943 2,536,462 Price Jan. 2, 1951 

